Ink supply with motion accumulator for stencil duplicator

ABSTRACT

An automatic inking system in a twin cylinder stencil duplicator including a movable ink stand having a disposable sealed ink container mounted thereon and an indexing mechanism operatively connected to the stand for effecting step-by-step movement of the ink container against its cover which acts as a piston. The indexing mechanism is actuated in response to a predetermined and preset number of revolutions of the main shaft of the machine thereby adjusting the inking rate in accordance with paper type and degree of coverage required.

ite States atent- 1191 Bosshardt 1 Apr. 16, 1974 1 INK SUPPLY WITH MOTION 3,154,218 10/1964 Aubert 222/70 ACCUMULATOR FOR STENCIL 3,133,673 5/1964 Buss 222/70 2,143,886 1/1939 Kline 101/366 DUPLICATOR 1,598,759 9/1926 Wilson... 101/366 [75] Inventor: William Bosshardt, Armonk, NY. 396,4 l/1889 erby..- 0 /366 362,966 5/1887 Hyatt 101/366 UX 1 Asslgheel Bohm Benton -9 Mlneola, 3,345,943 10/1967 Rakowicz.. 101/366 3,312,165 4/1967 Strorn 101/119 [22] 1971 3,090,302 5 1963 Johnson 101/366 x [21] Appl. No,: 191,369 FOREIGN PATENTS OR APPLICATIONS Related US. Appli a n a 789,785 1/1958 Great Britain 101 366 [62] Division of Ser. No. 873,042, Oct. 31, 1969, Pat. No.

3,652,083. Primary ExaminerRobert E. Pulfrey Assistant ExaminerR. E. Suter [52] US. Cl 101/122, 101/119, 101/366, Attorney, Agent, or Firm-Amster and Rothstein 222/52 [51] Int. CI B411 13/08, B4lf 31/02 [57] ABSTRACT [58] Field of Search 101/366" 122; An automatic inking system in a twin cylinder stencil 222/52, 611 1621 385; 74/84 duplicator including a movable ink stand having a disposable sealed ink container mounted thereon and an [56] References C'ted indexing mechanism operatively connected to the UNITED STATES PATENTS stand for effecting step-by-step movement of the ink 3,608,483 9/1971 Kaminstein .L 101 /366 Container against its Cover Which acts as a piston- The 2,821,910 2/1958 Mazzio et a1. 101 132.5 indexing mechanism is actuated in response to a pre- 3,521,560 7 1970 SchmidIin et a1. 101/145 determined and preset number of revolutions of the 3,242,860 3/1966 Gates 101/366 main haft ofth machine thereby adj tingthe inking 25/871216 4/1957 Gaes 101/366 rate in accordance with paper type and degree of cov- 3,439,609 4/1969 Dorr 101/366 erage required 2,893,318 7/1959 Kreher.... 101/366 1,081,429 12/1913 BuIIis 101/366 X 5 Claims, 11 Drawing Figures PATENTEBAPR 16 1914 3.80%012 ATTORNEYS PATENTEDAPR is 1924 SHEEI 3 BF 7 PATENTEB APR 16 I974 3 we: 7 OF 7 INK SUPPLY WITI'I MOTION ACCUMULATOR FOR STENCIL DUPLICATOR This application is a division of copending U.S. patent application Ser. No. 873,042, filed Oct. 31, l969 now U.S. Pat. No. 3,652,083 and assigned to the same assignee.

The present invention relates generally to printing machines, and in particular to a twin cylinder stencil duplicator for printing from a stencil master.

Among the equipments available for producing relatively large numbers of copies at relatively low cost are the so-called single cylinder and twin cylinder stencil duplicators, also known as mimeograph machines. In the typical single cylinder machine, there is provided a hollow inking drum which is perforated in its cylindrical surface and provided with an ink pad through which ink penetrates through a stencil mounted on the drum to the paper sheets as they are fed. The second type is the twin cylinder stencil duplicator in which two cylinders are mounted in spaced parallel relation around which a silk screen stencil carrier is mounted. Provision is made for applying a sufficient amount of ink to the surface of the cylinders for transfer to the copy paper through the silk screen and thereafter through the stencil and onto the impression paper during the printing function.

Twin cylinder stencil duplicators can use a viscous paste ink which tends not to leak and produces good quality mimeograph copies. They can be operated by untrained office personnel with little instruction. The fully automatic stencil duplicators that minimize the skills required by the operator have steadily become more complex mechanically and more expensive until in some cases they approach the cost of offset duplicators. However, if it were possible to provide a twin cylinder duplicator of simplified design and comparatively low cost which was easy to operate and could produce good quality copies with minimum operative complexity and servicing requirements, such a machine would find broad acceptance.

Accordingly, it is an object of the present invention to provide a twin cylinder stencil duplicator which realizes one or more of the aforesaid objectives. Specifically, it is within the contemplation of the invention to provide a twin cylinder stencil duplicator which provides all the functional, sensing and control features for machines of this type, yet is of relatively simple construction and is capable of mass production manufacture at arelatively low unit cost.

It is a further object of the invention to provide an improved duplicating machine of this type which incorporates an automatic inking system with the capability of adjusting inking rate in accordance with paper type and degree of coverage required.

In accordance with the present invention, provision is made to provide the requisite ink supply for all machine speeds and copy characteristics. Ink feeding re quirements vary as a function of copying speed, type of paper being printed and the degree of ink coverage for the copy being duplicated. Advantageously, the present machine incorporates an automatic inking system which is much less complicated than comparable systems on existing twin cylinder equipments, is reliable and trouble-free in operation and is readily adjusted by the operator to provide the amount of ink required.

The machine includes a movable ink stand having a disposable sealed ink container mounted thereon. An indexing mechanism is operatively connected to the stand for effecting step-by-step movement of the ink container against its cover which acts as a piston, to supply ink in discrete amounts. Actuating mechanisms, including motion transfer means, are operatively connected to the indexing mechanism and are operative in response to a predetermined and preset number of revolutions of the main shaft of the machine for imparting an indexing stroke to the indexing mechanism to effect ink dispensation. By a simple manual adjustment, the operator can preset the automatic inking mechanism to deliver more or less ink to the printing mechanisms in accordance with various printing requirements. Alternately, the automatic inking can be disengaged and ink provided by a hand-operated lever.

The above brief description, as well as further objects, features and advantages of the present invention will be more fully appreciated by reference to the following detailed description of a presently preferred, but nonetheless illustrative embodiment demonstrating the present invention, when taken in conjunction with the accompanying drawing, wherein:

FIG. 1 is a front elevational view of an improved duplicating machine embodying features of the present invention, with some parts broken away;

FIG. 2 is a diagrammatic view taken longitudinally through the machine and showing the relationship of the paper feeding and paper control mechanisms at the start of paper feed;

FIG. 3 is a view similar to FIG. 2 but further advanced in the paper-feeding cycle;

FIG. 4 is a medial sectional view, on an enlarged scale, taken substantially along the line 4-4 of FIG. 1 and looking in the direction of the arrow;

FIG. 5 is an elevational view taken from the left of FIG. 1 as indicated by the directional arrow, with the left cover removed and the front and rear covers swung to their respective open positions and showing the mechanisms mounted on the left side plate of the machine;

FIG. 6 is an enlarged elevational view similar to FIG. 5 but with parts removed for clarity;

FIG.-7 is an elevational view of the right side of the machine taken along the directional arrow 12 in FIG. 1, with the right side cover removed, with the front and rear covers shown respectively in their open positions and illustrating the mechanisms mounted on the outer side of the right side plate of the machine;

FIG. 8 is an enlarged elevational view of a portion of the mechanisms shown in FIG. 7;

FIG. 9 is a sectional view, on an enlarged scale, taken substantially alongthe line 9-9 of FIG. 7;

FIG. 10 is a sectional view taken substantially along the line 10l0 of FIG. 1, with parts broken away, showing the mechanisms mounted on the inner side of the right side plate of the machine;

FIG. 11 is a sectional view taken along the line 11-11 of FIG. 10 and looking in the direction of the arrows.

Referring now specifically to the drawings, and in particular to FIGS. 1 to 6, the present duplicating machine, which is generally designated by the reference numeral 30, is seen to include a housing 32 having a pivoted front cover and paper feed tray assembly 34 (see FIG. 4), a pivoted rear cover and paper-receiving tray assembly 36, a removable left side cover 38 mounted to house the mechanisms supported on the left side plate 40 ofthe machine and a removable right side cover 42 mounted to house the mechanisms mounted on the right side plate 44 of the machine. Straddling the machine is a removable front top cover 45 which is mounted on the left and right side plates, as by easily disengaged machine screws. As seen best in FIG. 5 and as shown by the dotted lines and indicated by the respective directional arrows, the front cover and tray assembly 34 and the rear cover 36 may be swung to their respective closed positions wherein they cooperate with the remainder of the housing 32, including side covers 38, 42 and front top plate 45 to completely enclose the duplicating mechanisms and to form a dust-proof case. The front cover and tray assembly 34 is pivotally mounted at opposite side pivots which are in turn movably mounted on the frame of the machine such that assembly 34 may be swung to its horizontal and operative position. The rear cover 36 is directly pivoted on the frame of the machine at side pivots 48 and may be swung about its pivots to a horizontal position projecting rearwardly of the machine 30 in which position it serves as thereceiving tray for the machine.

The front cover and feed tray assembly 34 is operable successively to deliver the topmost sheet from a paper stack along a predetermined feed path to the duplicating mechanisms of the machine.

Assembly 34 includes a tray platform 50 which includes top platform wall 52 and bottom platform wall 54 which are spaced apart and define a mechanismreceiving housing H therebetween. Projecting upwardly from and movably mounted on platform 50 (which is horizontal in the operative position of the machine) are left and right paper guides or tray sides 56, 58 which are adjustable towards and away from each other in accordance with stack width to laterally position and guide the paper stack therebetween. The symmetrically disposed and adjustable tray sides 56, 58 respectively include upstanding guide flanges 56a, 58a and horizontal support flanges 56c and 580, the latter overlying and resting against the top platform wall 52.

Extending from side to side of the machine at a location spaced in the direction of feed from the tray platform 50 is a horizontal fixed feed table 60 along which the topmost sheets pass in succession to the duplicating mechanisms 62. Fixed feed table 60 is fixed to the opposite side plates 40, 44 of the machine in any appropriate fashion and is at a fixed level in relation to the duplicating mechanisms 62 for guiding the topmost sheets along the requisite feed path to the duplicating mechanisms 62.

Fixed to and depending from feed table 60 is an upstanding stack-abutment wall 64 against which the leading end edges of the stack of paper stock S abuts when the feed tray is loaded; The stack-abutment wall 64 is mounted such that it may serve as an unobstructed guide track for left and right corner separator assemblies 66, 68 which are of identical and mirror image construction and are symmetrically disposed relative to the longitudinal center line of the adjustable tray 50, and side guides 56, 58.

The corner separator assemblies 66, 68 are laterally adjustable in two ways: simultaneously with and independently of the respective side guides 56, 58. At any adjusted position of the side guides 56, 58, the corner separator assemblies 66, 68 are independently adjustable to overlap the left and right front corners of paper stack S in varying amounts in order to provide adjustable interference at the front corners of the stack S to assure proper feed for different paper weights and stiffness, machine feed rate, etc.

Turning now to a consideration of the machine's main drive, as shown in FIG. 1, there is provided a main shaft 98 which extends from side to side of the machine above the tray assembly 34 and forwardly of the duplicating mechanism 62 and is journalled in appropriate bearings on the opposite side plates 40, 44 of the machine. Main shaft 98 extends through the right side plate 44 and through the right side cover 42 and carries a disengageable handle 100. Additionally, main shaft 98 extends beyond left side plate 40 into the adjacent housing where it carries, in succession from plate 40 outwardly, idler-actuating cam 102, impression roller release cam 104, main drive gear 106 and second feed roller drive cam 108. In lieu of manual turning of the main shaft 98 by crank 100, provision is made for a motor to drive main drive gear 106. As seen in FIGS. 1 and 4, the motor and reduction gear assembly and related parts are all behind front top plate 45 and coupled by obvious reduction and coupling arrangements I12, 114, 116, 118, 120 and 122 to driving pinion 124 engaging main drive gear 106. Spring clutch 126 is provided such that the motor and reduction gears are effectively decoupled from the main drive and main shaft 98 when the machine is turned by crank 100.

The machine may be provided as either handoperated or motor-driven. However, since motor 110 and all related components, including reduction gearing, clutch, controls (i.e., controls 394, 396) are all mounted on front top plate 45, a manually operated machine may be converted to motorized operation by the simple substitution of the appropriate top plate 45 containing the motor and related components and utilizing predrilled holes in the left side plate 40 of the machine frame for wiring and line plug.

Moving along the paper feed path to the duplicating mechanisms 62, there is provided a second pair of feed rollers 224, (only one of which is shown is FIG. 4) which are received in corresponding cutouts formed in feed table 60, with feed rollers 224 being faced with rubber or any other appropriate elastomeric material and projecting through the cutouts to contact the bottom of the sheet being fed into duplicating mechanisms 62. The second pair of feed rollers 224 is fixed to a feed roller shaft 228 appropriately journalled on the side plates 40, 44, with the shaft extending into the housings at the left and right of the machine, as seen in FIGS. 5 and 7. As shown in FIG. 6, drive is periodically imparted to feed roller shaft 228 from the main shaft 98 of the machine via an adjustable lost-motion mechanism which includes driving rack 230, drive gear 232, coiled biasing spring 234, follower lever 132 to produce lost motion travel of tab 132a relative to follower 230e, and permits the adjustment of the sheet feed in relation to the duplicating mechanisms 62 to achieve varying registrations between the sheets fed and the stencil or master, as shown in US. Pat. No. 3,652,083.

Successive sheets of paper are clamped against the feed rollers 224 by an idler or pinch roller assembly which includes a plurality of pinch rollers 236 (FIG. 4) mounted on a pinch roller shaft 238 journalled coaxially with pivots 180, 182. To feed paper, pinch rollers 236 are rocked in the counterclockwise direction about their pivots; as shown diagrammatically in FIGS. 2 and 3, pinch rollers 236 engage the sheet of paper trapped between feed rollers 224 and the pinch rollers. The sheet is fed into duplicating mechanisms 62 in response to actuation of the second feeding rollers 224. The pinch rollers 236 are raised and lowered under control of cam 102, FIGS. 1 and 4, through provision of cam follower roller 240 mounted on follower arm 242, which projects through cutout 40f in side plate 40and engages cam 102. Follower arm 242 is rigidly connected to the shaft 238 carrying the mounting brackets 244 for the pinch rollers 236.

Projecting above feed table 60 at a location substantially corresponding to the bight of the second feed rollers 224 and the pinch rollers 236 is a paper stop 246 which is pivoted at 248 and biased into its paperblocking position by spring 250 (see FIG. 4). Stop 246 carries an actuating pin 252 which is in position to be engaged by depending finger 244a on mounting bracket 244 such that in response to clockwise turning movement of bracket 244, and engagement of the pinch rollers 236 with the second feed rollers 224, stop 246 is withdrawn from the feed path to permit unobstructed paper feed, as seen in FIGS. 2 and 3.

It will be appreciated that the time in the machine cycle that drive is imparted to the second feed rollers 224 in relation to the initiation of any particular machine cycle will determine the position of the leading edge of the paper in relation to the image on the master mounted on the duplicating mechanisms 62. This relative position is controlled by the adjustable lost-motion mechanism.

The final aspect of the paper feeding system includes impression roller 266 (FIG. 4) which is separated from the duplicating mechanisms 62 during the non-printing part of the machine cycle under control of an impression roller blocking assembly 268. Considering first the impression roller 266 and its actuating mechanism, the impression roller 266, which has an appropriate elastomeric face, is mounted on impression roller shaft 270 which in turn is journalled on one arm of a bell crank 272 which is pivoted at 274 on the machine frame. The other arm of bell crank 272 is connected to a doublearm follower lever 276 which is pivoted at 274 on the outer side of left side plate 40 (see FIG. 6). Lever 276 is connected at pivot 278 to bell crank 272 through window 40g in the left side plate 40 (see FIGS. 4 and 6). Double-arm follower lever 276 carries a follower 280 which engages impression roller release cam 104 on main cam shaft 98. As seen in FIG. 5, an impression roller tension spring 282 is mounted by an appropriate bracket 284 on the left side plate 40 and is coupled at mounting tab 276a to the double-arm lever 276. Spring 282 is effective, when released for activation under control of cam follower 280, to turn pivot 278 at the lower end of double-arm lever 276 in the clockwise direction (see FIG. 6) to thereby turn the bell crank 272 (see FIG. 4) in the counterclockwise direction to raise the impression roller 266 into contact under pressure with the duplicating mechanism 62. The pressure on the impression roller 266 is determined by the adjustment of coil spring 282, as is generally understood.

Basically, the impression roller 266 includes an inoperative position illustrated in FIG. 4 and shown diagrammatically by the full lines in FIGS. 2 and 3, an operative position 266' against the duplicating mechanisms as shown by the dotted lines in FIG. 3 and an intermediate position 266 established under control of the blocking assembly 268 which, if it does not sense a partially fed sheet, blocks the impression roller 266 from contacting the duplicating mechanisms 62 and picking up an inked impression which would foul the impression roller 266. The blocking assembly 268 which achieves this function includes a sensing finger 268a and a follower lever blocking arm 2681; (see FIG. 4) which are rigid with each other and mounted on a single shaft journalled on the machine frame at pivot 268s. Blocking arm 268b extends through cutout 4011 in the left side plate 40 in position to be contacted by a tab 276b on cam follower arm 276. Thus, as cam follower arm 276 begins to move from its fully retracted position (shown by the dot-dash showing to the left of the full line illustration in FIG. 6) to the full line illustration, the blocking member 268b will block follower 280 from following cam 104 (as shown by the dot-dash showing at the left of FIG. 6), thereby establishing the blocked position for impression roller 266 wherein the machine rotates, but impression roller 266 is not fouled due to the failure of a sheet of feed.

Duplicating mechanism 62 is in the form of a twin cylinder, silk screen assembly (see FIG. 4), including upper cylinder 286 mounted on upper cylinder shaft 288 and lower cylinder 290 mounted on lower cylinder shaft 292. The twin cylinder assembly 62 carries the usual mechanisms for attaching a stencil master to the silk screen, and for connecting both cylinders with a suitable belt drive for simultaneous rotation of the entire assembly. As seen in FIG. 5, drive is imparted to the lower cylinder shaft 292 by cylinder drive gear 294 which is driven from main drive gear 106 and transferred to the upper cylinder and silk screen in a conventional manner not shown.

Disposed between the upper and lower cylinders 286, 290 are the usual ink-spreading rollers 296, 298 and a removable and replaceable ink distributing tube 300. Reference will now be made to FIGS. 7, 9 and 10 for a description of the mechanisms which axially reciprocate the ink-spreading rollers 296, 298 during machine operation. At the right side of the machine, right side plate 44 is provided with appropriate cutouts 44c, 44d through which roller shafts 296a, 298a project. Shafts 296a, 298a are provided with circumferential grooves and receive respective oscillating arms 302, 304 which are pivoted at 302a, 304a on a common actuating yoke 306. Oscillating arms 302, 304 are biased toward each other and into engagement with shafts 296a, 298a by spring 308, with limits being established by stops on yoke 306. As seen in FIG. 7, yoke 306 is pivoted on the outer side of right side plate 44 by brackets 310,312 which afford yoke pivots at 314, 316. Yoke 306 is rocked about the coaxial pivots 314, 316 from the main shaft 98 through the provision of a wobbler mechanism which includes (see FIG. 9) angularly disposed wobbler drive discs 318, 320 fixed to shaft 98 and having an oscillating Wobbler plate 322 trapped therebetween. Wobbler plate 322 is coupled to a right angle connecting tab 306a on rocker arm 306b integral with yoke 306 by an appropriate connecting pin 324. Thus, in response to rotation of main shaft 98, reciprocal motion will be imparted to the ink rollers 296, 298, which are simultaneously rotated by cylinders 286, 290. By the simple expedient of spreading the oscillating arms 302,

304 against their bias of spring 308, the rollers may be removed.

Reference will now be made to the mechanisms for supplying ink to the ink distributing tube 300, both manually and automatically during machine operation. As shown in FIG. 7, the ink distributing tube is a conventional unit which includes internal provision for regulating the ink supply to the cylinders 286, 290 through control knob 326. The assembly of ink tube 300, related gears, and knob 326 are all mounted on a common carrier plate 332 which is slidably and removably mounted on a supporting bracket 334 fixed to the outer side of right side plate 44. Additionally, carrier plate 332 supports a depending and fixed ink supply tube 336 which connects with the interior of an ink-supply cartridge 338 including a container, such as 338a and a cover 3381; serving as a piston. In response to movement of the cover 338b from its upper position when can 338a is full to a lower position contiguous to the bottom of the can, the ink I therein is forced upwardly through ink supply tube 336 and into tube 300. Ink supply tube 336 carries a pressure plate 340. As is generally understood, can 338a of cartridge 338 moves upwardly relative to the piston cover 3381). This movement progressively supplies ink to distributing tube 300. To this end, there is provided a rising ink stand 342 which includes cartridge-supporting platform 342a and upstanding carrier 342b appropriately mounted for vertical movement on a mounting bracket 344 fixed to right side plate 44. At its rearward side, the ink stand 342 is provided with a rack 342c which is engaged by elevating pinion 348 on pinion shaft 350. Pinion shaft 350 also carries elevating ratchet 352 which is engaged by actuating pawl 354 and holding pawl 356. A downward stroke imparted to actuating pawl 354 turns ratchet wheel 352 counterclockwise driving the elevating piston 348 in the same direction and lifting the cartridge supporting platform 342a for extruding ink from cartridge 338 through ink tube 346 onto the cylinders 286, 290. Holding pawl 356 is pivoted at 356a on right side plate 44 and is urged by gravity into its holding position. Holding pawl 356 includes a disabling tab 356b which is in the path of upward movement of the pawlrelease finger 342d on platform 342 such that the holding pawl 356 is lifted clear of the elevating ratchet 352 when cartridge 338 is empty.

The machine includes systems for imparting the downward actuating stroke to actuating pawl 354, both manually and automatically. The automatic inkpumping system includes a mechanism which adjusts the frequency of pumping strokes to actuating pawl 354 over a wide range for providing the required amount of ink to the printing mechanisms 62. The adjustment can range from one stroke for ten machine cycles to one stroke for 70 machine cycles, depending upon the ink required for the stencil master used.

The manual ink supply system includes (see FIG. 10) a forwardly extending ink supply lever 358 mounted inwardly of the right side plate 44 of the machine beneath the top cover plate 45 with the lever having a finger tab 358a in a convenient position at the front of the machine to be depressed by the operator (see FIG. I) as ink is required. Lever 358 is pivoted at 360 on the inner side of plate 44 and is coupled by a connecting link 362 through cutout 44c to pawl-actuating lever 364 pivoted on the outer side of plate 44 at pivot 366. Connecting link 362 has an override slot 362a at one end to receive actuating pin 358f on lever 358. The opposite end of connecting link 362 is pivotally connected to one arm of the pawl-actuating lever 364 by pin 368, with the other arm of lever 364 being connected at pivot 370 to actuating pawl 354. Spring 372 (FIG. 7) biases actuating pawl 354 against elevating ratchet wheel 352. Thus, upon depressing finger tab 358a, manual ink supply lever 358 turns in the clockwise direction about its pivot 360 and pin 358b bears against the outer end of slot 362a to pull upwardly on connecting link 362. This motion is transmitted via pawl-actuating lever 364 into a downward supply stroke on actuating pawl 354 to elevate ink stand 342a through rotation of ratchet wheel 352.

When pawl-actuating lever 364 is actuated automatically to achieve a supply stroke, override slot 362a effectively isolates the movement of connecting link 362 from supply lever 358 which remains stationary.

The automatic ink-supply system is adjustable by the operator and provides supply strokes to the actuating pawl 354 after any predetermined number of machine cycles and is seen best in FIGS. 7, 8 and 9. A doublearm cam follower lever 374 pivoted at 366 and one arm carrying follower roller 376 adjustably engages cam 202 on main shaft 98, and the second arm of lever 374 is connected via a motion input link 378 to a motion transfer mechanism 380 which periodically imparts an actuating motion to a motion output link 382. When link 382 is moved, one arm of the ratchet-actuating lever 364 automatically depresses pawl 354 to provide an automatic supply of ink. Such supply strokes are provided after a preset number of machine cycles, as determined by the adjustment ofa slidable finger piece 384 mounted beneath the front cover 45 of the machine (see FIGS. 1, 7 and 10). Specifically, motion input link 378 is adjusted by a sliding camming plate 386 to control the stroke of lever 374 at pivot 375. Bias spring 388 urges follower 376 toward cam 202 at the adjusted clearance position determined by adjustment of link 378 via a stroke-adjustment tab 378a which extends through cutout 44f on the side plate 44. This adjustment will be described subsequently in conjunction with FIGS. 8, l0 and 11. Input link 378 has a pivotal connection at 390 to the drive arm 380a of the motion transfer mechanism 380 which is a form of one-way clutch which precludes backlash.

Referring now to FIGS. 8 and 9, the motion transfer mechanism 380 which receives its input from link 378 via actuating arm 380a includes a fixed central pin 380b on which is journalled an inner driving raceway member 380C. Surrounding driving raceway member 3800 is an outer raceway member 380d. Plural clutch rollers 380e are interposed between raceway members 380e, 380d and have appropriate seats 380f on member 380d. In response to clockwise turning motion of the driving raceway member 3806 (see FIG. 8) by upward motion of input link 378, interposed rollers 380e via seats 380fturn the driven raceway member 380d in the clockwise direction. This in turn imparts incremental motions in the clockwise direction to the diametrically opposed driving pins 380g, 380h which, after of rotation, are coupled in succession to the output motion link 382 at seating cutout 382a. Thus, in response to incremental motions imparted to motion input link 378 from cam follower 376 (which incremental motions are indicated by the multiple small clockwise arrows in FIG. 8), the driving pins 380g, 380h periodically come into link cutout 382a to pull the link 382 through an actuating stroke which is sufficient to impart a supply stroke to actuating link 354 for the requisite automatic supply motion to ratchet wheel 352.

In order to assure that the motion transfer mechanism 380 will accurately accumulate and transfer the incremental clockwise motions imparted thereto, any appreciable backlash or counterclockwise motion must be avoided. Backlash would tend to cancel the small incremental accumulations duringeach machine cycle, and therefore a holding raceway member 380i is provided surrounding the driven raceway member 380d. Member 380i is fixed by mounting arm 380j and anchor pin 380k to the right side plate 44. Interposed between the driven raceway member 380d and the stationary holding raceway member 380i are plural clutch roller 3801 which bear against seats 380m on member 3801' and oppositely arranged to seats 380f. Thus, driving motion is accumulated in the mechanism 380 and passed to driven raceway member 380d and thence to the motion output link 382 in response to clockwise input, with all counterclockwise motion effectively blocked by the counteracting rollers 3801 which wedge against the stationary seats 380m on holding raceway member 380i.

From the foregoing it will be appreciated that the total stroke of motion input link 378 is determined by the throw of cam 202 and the adjusted position of follower roller 376 relative thereto. Thus, if follower roller 376 moves quite close to cam 202, it will contact a rising cam surface sooner and provide a greater upward thrust to motion input link 378. Link 378 is biased by spring 388 to move cam follower 376 in the counterclockwise direction about pivot 366 (see FIG. 7) into a limit position close to cam 202 determined by the bottom Wall of cutout 44f. As link 378 is moved upwardly by adjustments of tab 378a, less and less of the total throw of the cam 202 is transmitted via follower 376 to motion input link 378 and the clockwise incremental motions to arm 380a correspondingly decrease. Accordingly, it will take a greater number of machine cycles and rotations of cam 202 to accumulate sufficient motion in mechanism 380 to drive output link 382 between its full and broken line positions which correspond to one step of .the elevating ratchet 352 to provide a predetermined supply of ink into the ink distributing tube 300. As previously pointed out, adjustment of tab 378a is accomplished by the slidable inking control finger piece 384 on the front top plate 45 of the machine. Referring now to FIGS. 1, 10 and 11, the inking control finger piece 384 is seen to be mounted for side-to-side sliding movement by a mounting block 384a which extends into cutout 45a on top plate 45. Connected to finger piece 384 is a camming plate 386 having an angularly disposed camming ledge 386a. Camming ledge 386a is engaged by cam follower 389 which is pivoted at 391a to rock about a substantially horizontal axis in response to side-to-side displacement of cam plate 386. Cam follower bracket 389 includes a cam follower arm 389a (see FIG. 10) which engages the cam ledge 386a and an output arm 38% (see FIG. 11) disposed in spaced parallel relation to the follower arm 389a and substantially at right angles thereto in position to lie beneath and engage adjustment tab 378a on motion input link 378. As finger piece 384 is pushed to the right (see FIG. 1), follower arm 389a will turn in the counterclockwise direction about pivot 391a (see FIG. 10) to lower arm 38% and permit tab 378a to drop under bias of spring 388. This in turn brings cam follower roller 376 closer to its actuating cam 202 and thereby utilizes a greater portion of the cam throw, and provides a more rapid accumulation of rotary motion in mechanism 380 which is translated into more frequent pumping action of the automatic ink-supply system. correspondingly, adjustment of finger piece toward the left in FIG. 1 utilizes less of the cam throw and a corresponding slower motion accumulation and a less frequent pumping action.

Disposed above the finger piece 384 on the top plate 45 is a motor control panel 392 which includes a motor on-off push-button 394 and a speed control knob 396 controlling the usual rheostat (see FIG. 11). Motor pushbutton 394 turns the motor 1 10 on and off through a conventional circuit and switch. Additionally, pushbutton plunger 394a is coupled to the handle or crank on main shaft 98. As seen best in FIG. 9, handle or crank 100 includes an inwardly facing coupling collar 100a which is provided with diametrically opposed cutouts 100b which receive corresponding pins 98b on shaft 98. Outward displacement of handle 100 on shaft 98 (to the left in FIG. 9) decouples handle from shaft 98. This is accomplished in advance of energization of the motor 1 10 to assure that the handle 100 will not rotate during motorized operation. As seen in FIG. 11, plunger 394a engages crank-disengaging double-arm lever 400 which is pivoted by appropriate bracketing at 402 and is connected to a pull rod 404 at pivot 406. Pull rod extends through cutout 44g in the right side plate 44 and engages a double arm actuating lever 408 (see FIGS. 7 and 9) which is pivoted at 316 and includes arm 408a which displaces the handle 100 in advance of motor turn-on. Provision is made intermediate lever 408 and push rod 404 for achieving adjustment of the position of lever 408 to the extent required to assure complete handle disengagement in response to rocking motion of lever 408.

For operator convenience, three ways are provided for feed turn-off: manually by pushing button 412, automatically in response to countdown of a counter 438 and automatically when the paper supply in tray 50 is exhausted as signalled by the position of slide block 92b.

What is claimed is:

1. An automatic inking mechanism for a printing machine including a rotatable main shaft comprising a movable ink stand, an ink container mounted on said stand adapted to contain a supply of ink and including a cover, an indexing mechanism operatively connected to said stand for effecting stepwise relative movement of said container and cover to dispense ink from said container in discrete amounts and actuating mechanisms including motion transfer means operatively connected to said indexing mechanism and operable in response to each of a series of revolutions of said main shaft for accumulating a series of incremental rotary motions and after said series of incremental rotary motions have been accumulated, transferring an indexing stroke to said indexing mechanism to effect ink dispensation, said motion transfer means including a one-way clutch having a driving raceway member, a driven raceway member and clutch rollers interposed therebetween, and said actuating mechanism further including motion input means actuated in response to each revolution of said main shaft and connected to said driving raceway member for imparting incremental rotary motion thereto and motion output means coupled to said driven raceway member and to said indexing mechanism for providing said indexing stroke after transfer to said one way clutch of said series of incremental rotary motions.

2. An automatic inking mechanism according to claim 1 wherein said motion transfer means further includes an anti-backlash mechanism operatively connected to said one-way clutch and arranged to preclude rotation in a direction opposite to the direction of said incremental rotary motion.

3. An automatic inking mechanism according to claim 2 wherein said anti-backlash mechanism includes a fixed holding raceway member surrounding said driven raceway member and clutch rollers interposed between said holding raceway member and said driven raceway member.

4. An automatic inking mechanism according to claim 1 wherein said actuating mechanisms includes an actuating cam on said main shaft, a follower adapted to engage said actuating cam, motion input means actuated in response to movement of said follower and operatively connected to said motion transfer means and means for adjusting said motion input means to initially position said follower relative to said cam to vary the amount of motion imparted to said motion transfer accumulating means from said cam and follower during each revolution of said main shaft.

5. An automatic inking mechanism according to claim 1 further including manual actuating means and means including a lost-motion coupling for imparting indexing strokes to said indexing mechanism in response to operation of said manual actuating means, said lost-motion coupling serving to decouple said manual actuating means from said indexing mechanism during operation of said actuating mechanisms.

Patent Non .mventofls) William BOSShEfifdw.

, I: is cer'tified' that errnr appears in above identifiefi patent and that sai LEiZfiEZS Pawn? are hereby fifill''fifiied ag; shown balms:

0n the first page, the fifth 0f the left colmm, Item N0. {73] delete "Bob-m" and substitute therefor Bo'hn Attesc:

C. MARSHALL DANN MCCOY M GIBSON, JR

jCommissioner of Patents 4 Attescing Officer 

1. An automatic inking mechanism for a prinTing machine including a rotatable main shaft comprising a movable ink stand, an ink container mounted on said stand adapted to contain a supply of ink and including a cover, an indexing mechanism operatively connected to said stand for effecting stepwise relative movement of said container and cover to dispense ink from said container in discrete amounts and actuating mechanisms including motion transfer means operatively connected to said indexing mechanism and operable in response to each of a series of revolutions of said main shaft for accumulating a series of incremental rotary motions and after said series of incremental rotary motions have been accumulated, transferring an indexing stroke to said indexing mechanism to effect ink dispensation, said motion transfer means including a one-way clutch having a driving raceway member, a driven raceway member and clutch rollers interposed therebetween, and said actuating mechanism further including motion input means actuated in response to each revolution of said main shaft and connected to said driving raceway member for imparting incremental rotary motion thereto and motion output means coupled to said driven raceway member and to said indexing mechanism for providing said indexing stroke after transfer to said one way clutch of said series of incremental rotary motions.
 2. An automatic inking mechanism according to claim 1 wherein said motion transfer means further includes an anti-backlash mechanism operatively connected to said one-way clutch and arranged to preclude rotation in a direction opposite to the direction of said incremental rotary motion.
 3. An automatic inking mechanism according to claim 2 wherein said anti-backlash mechanism includes a fixed holding raceway member surrounding said driven raceway member and clutch rollers interposed between said holding raceway member and said driven raceway member.
 4. An automatic inking mechanism according to claim 1 wherein said actuating mechanisms includes an actuating cam on said main shaft, a follower adapted to engage said actuating cam, motion input means actuated in response to movement of said follower and operatively connected to said motion transfer means and means for adjusting said motion input means to initially position said follower relative to said cam to vary the amount of motion imparted to said motion transfer accumulating means from said cam and follower during each revolution of said main shaft.
 5. An automatic inking mechanism according to claim 1 further including manual actuating means and means including a lost-motion coupling for imparting indexing strokes to said indexing mechanism in response to operation of said manual actuating means, said lost-motion coupling serving to decouple said manual actuating means from said indexing mechanism during operation of said actuating mechanisms. 